Rotary engine



A. E. KEF'PLER Feb. 6, 1968 ROTARY ENGI NE 4 Sheets-Sheet 1 Filed June 12 1965 lrl/I/l INVENTOR. ANTHONY E. KEPPLE/P A. E KEPPLER Feb. 6, 1968 ROTARY ENG INE 4 Sheets-Sheet Filed June 5, 1965 INVENTOR.

42 ANTHONY .5 K5

PPLER ,MMJ 1 1 H 5.

Feb. 6, 1968 A. E. KEPPLER 3,367,240

ROTARY ENG INE Filed June 1 1965 I 4 Sheets-Sheet "mlllllill /j 11/1114 INVENTOR. ANTHONY-E. KEPPLER 1 FHL 5.

Feb. 6, 1968 KEPPLER 3,367,240

ROTARY ENGINE Filed June 9, 1965 4 Sheets-Sheet 4;

INVENTOR. ANTHONY E KEPPLER United States Patent 3,367,240 RQTARY ENGINE Anthony E. Keppler, 2341 N. Commonwealth, Chicago, Ill. 60614 Filed June 9, 1965, Ser. No. 462,627 1 Claim. (Cl. 91-175) This invention relates generally to a hydraulic engine or hydraulic motor. More particularly, the invention pertains to a hydraulic engine actuated through the flow of pressurized incompressible fluid in a hydraulic system. The pump or other means relied upon to develop the necessary hydraulic pressure does not form a part of the present invention. In a particular preferred embodiment, the hydraulic engine of the invention includes as structural elements a pair of parallel laterally spaced floating rings which rotate in a plane which is other than transversely disposed with respect to the output shaft of the engine. The importance of this novel arrangement will become evident as the description of the invention proceeds.

The hydraulic motor or hydraulic engine of the present invention finds utility in all applications where it is desired to utilize pressurized hydraulic fluid as a power source. It is the aim of the invention to provide a compact and highly efficient machine which is substantially self-contained requiring external connections only for fluid circulation.

It is a principal object of the invention to provide a hydraulic engine in which a plurality of cooperating and interdependent cylinder and piston assemblies act in concert through hydraulic fluid pressure to drive an output shaft of the machine.

It is a related object of the invention to provide a machine in which a plurality of cylinder and piston assemblies extending parallel to an output shaft of the engine and displaced radially from that shaft are supported between laterally spaced floating rings which revolve about the output shaft.

Still another object of the invention is to provide a hydraulic engine in which the power output derived through reciprocal motion of pistons in cylinders is augmented by the reciprocal movement of the piston and cylinder assemblies themselves during operation of the engine.

Other and further objects, uses, and advantages of the invention will become apparent from a reading of the following specification taken in conjunction with the drawings in which:

FIGURE 1 is a top view, partly in section, and illustrating a preferred embodiment of the invention;

FIGURE 2 is a front view, partly in section,

FIGURE 3 is a cross sectional view taken substantially on the line 3-3 of FIGURE 2;

FIGURE 4 is a perspective view, with parts cut away;

FIGURE 5 is an enlarged view, partly in section, of the linkage between a piston of the engine and the output shaft driving gears;

FIGURE 6 is a cross sectional view illustrating the porting and venting between a cylinder and a floating ring supported on an output shaft of the engine; and

FIGURE 7 is a perspective view of a piston and cylinder assembly supported between opposed floating rings, and showing the linkage from a piston to a gear assembly driving the output shaft of the engine.

A preferred form of the present invention, provided for the purpose of illustrative disclosure and not by way of limitation, is depicted generally in FIGURES 1 through 4 of the drawings. FIGURES 5 through 7 illustrate specific portions of the machine. Referring more particularly to the drawings, there is shown in FIGURE 1 a fluid-actuated hydraulic engine 10 including a shell or housing 12 comprising a generally cylindrical casting "ice 14 open at one end and provided with a lapped coverplate 16, the latter being connected to close and seal the open end of the casting 14. In the particular structure illustrated, the casting 14 and the cover-plate 16 are each provided with integral mating flanges 24 and 26 fastened together by means of bolts 36. As illustrated in FIGURES 2 and 4, the cylindrical shell 12 is provided with a threaded opening 34 adapted for connection to a pressurized fluid supply line 33. The housing or shell of the engine is supported on legs 42, as illustrated in FIGURES 3 and 4.

An output shaft 50 is supported in bearings 54 and 56 on opposed end walls 60 and 62 of the casting 12, and one end 66 of the output shaft 50 extends through the wall 62 of the shell for coupling or connection to a device to be driven by the hydraulic engine. On the output shaft 50 bearings 70 and 74 which, in the preferred embodiment of the invention illustrated are ball races, are a pair of floating rings 76 and 78. Sleeve bearings or bushings 80 and 82, preferably integrally formed with the floating rings 76 and 78, extend outwardly therefrom to stabilize and firmly support the rings on the output shaft 50. As clearly shown in the drawings, and particularly as illustrated in FIGURES 2 and 6, the floating rings 76 and 78, although parallel to each other are pitched laterally or angled with respect to the output shaft 50. That is, the principal planes of the floating rings do not extend transversely of the output shaft but are oblique with respect thereto. The reason for this novel arrangement will become clear as the description proceeds.

Supported on and keyed to the output shaft 50 is a primary gear 86 axially supported on the output shaft 50 for rotation therewith. The primary gear 86 couples with and positively engages a cooperating gear 90 which is keyed and axially supported on for rotation with a secondary shaft or drive shaft 92 extending generally parallel to the output shaft 59. The drive shaft 92 is supported on the shell or casing 12 of the engine of bearings 96 and 93. Also carried on the drive shaft 92 and keyed for rotation therewith are a pair of laterally spaced bevel gears 102 and 104 positioned to engage, respectively, gear teeth 108 and 110 disposed annularly about the circumferential expanse of the floating rings 76 and 78, whereby, upon rotation of the output shaft 50, and the primary gear 86 keyed therewith, the secondary shaft or drive shaft 92 is driven through gear 90 to cause rotation of the floating rings 76 and 78 which are coupled to bevel gears 102 and 104 aflixed to the secondary.

shaft 92.

Disposed radially outwardly from the output shaft 50 and parallel thereto are a plurality of cylinder and piston assemblies which extend between and are connected to opposed laterally spaced floating rings 76 and 78. The cylinder and piston assemblies 120 are annularly disposed about the output shaft 50 and, as clearly illustrated in FIGURE 1, in the preferred embodiment of the engine shown, three such assemblies 120 are used. Each of the cylinder and piston assemblies is generally of the same construction, and the following description will, in substantive respects, apply to any.

As illustrated most clearly in FIGURES 2 and 4, each assembly includes a pair of coaxial laterally spaced cylinder sections and 132 and an elongated piston 136 sleeved in and slidably disposed in the cylinder sections 130 and 132 for reciprocal movement therewithin. Each of the cylinder sections is provided at its outward end with joinder means for connecting the cylinder sections 130 and 132 to the floating rings in fluid dealing and fluid coupling engagement. In the preferred embodiment of the invention illustrated, the joinder means 140 and 142 take the form of enlarged ball-like portions which seat pivotally in cooperating sockets 146 and 148 formed in the body 152 and 154 of the floating rings 76 and 78, the sockets 146 and 148 opening at inner surfaces 156 and 158 of the floating rings.

Referring now to FIGURE 6, the body (152 or 154) of the floating rings is provided with fluid ports and channels which communicate with the surface defining the sockets formed in the body. The ports and channels also communicate with the cylinder portions at either end of the piston and cylinder assemblies. As shown in FIG- URE 6, a preferred fluid channeling structure includes a fluid input channel or passage 162 communicating between the pressurized fluid reservoir 166 and a cavity 170 formed outwardly of the cylinder and in communication therewith. Fluid flow through the fluid inlet channel 162 and into cavity 170 communicating with cylinder section 132 is controlled by means of a spring-biased valve 174, shown in an open position in FIGURE 6. The opening and closing of valve 174 is regulated through a camming surface 176 formed on a cam 178. The cam 178 is fastened to a flange integral with the stationary bushing-like sleeve which encircles output shaft 50 so that the earn 178 remains fixed in position as the body 152 of the floating ring 78 rotates. A valve spring 180 biases the valve cylinder 182 into stressing engagement with the camming surface 176, so that, in the open position of valve 174 depicted in FIGURE 6, high pressure hydraulic fluid is forced through cavity 170 into the cylinder section 132 and against the piston rod 136 to drive the rod to the left. At the particular phase of the cycle illustrated, fluid discharge from cavity 170 through channel 184, through the chamber of valve 188 and to passage 190 is blocked by the closed relief valve 188. However, at a subsequent portion of the cycle, fluid exhaust from the cylinder section 132 is through the channel 184, through the chamber of valve 188, and to passage 190, fluid flow being regulated and controlled by means of the spring-biased relief valve 188 the opening and closing of which is effected through a second camming surface 186 formed on the cam 178. During the fluid exhaust portion of the cycle the cam surface 186 causes compression of the valve spring of valve 188 to urge the valve body downwardly past the channel 184 to unblock the passage leading to passage 190. That is, the earn 178 closes and opens the valve 188 at a 180 phase relationship as compared with the timing of valve 174. The passage 190 vents through an exhaust port 196 (FIGURE 4). Since the fluid delivery to and exhaust of fluid from the cylinder portions at either end of the several cylinder and piston assemblies is achieved in the same manner for each cylinder section, and since the structure involved is generally the same, repetition of the detailed description has been avoided. Moreover, in the light of the foregoing disclosure, it will be clearly evident to those skilled in the art how the fluid input and fluid exhaust from the cylinder is controlled. Also, the specific technique relied upon for venting and for controlling valve operation is not critical and other well known engineering techniques may be utilized. The control and regulation of fluid flow to and from the cylinders is sequentially programmed so that the various pistons move in a coordinated and cooperating manner to supplement one another so that the overall resultant will be a smooth and positive rotation of the output shaft. The manner in which the output shaft is driven through the reciprocal action of the pistons is described below.

Referring now to FIGURES 1, 2, 4 and 5, and as shown in FIGURE 7, a sleeve 202, disposed about the output shaft 50 as a bushing, is fixed to and extends from a wall 60 of the housing or casing 12 of the machine. At its free end the sleeve 202 is joined to and immovably supports a fixed bevel gear 206 which is secured against rotation with respect to the casing or shell of the machine. A

spider 210 (FIGURE 3) is rigidly fixed to and supported on the output shaft 50 for rotation therewith. In the preferred embodiment of the invention illustrated, the spider 210 includes three arms or stud shafts 216 extending radially from and equally spaced about the output shaft 50. Each stud shaft 216, directed to a corresponding cylinder and piston assembly 120, rotatably supports a bevel gear 222. Each of the bevel gears 222 meshes with the fixed bevel gear 206 for engagement therewith and planetary travel therearound.

Each of the pistons 136 is connected to a corresponding rotatable bevel gear 222 by means of a linkage 230 which, in the preferred embodiment of the invention illustrated, comprises a rod or arm 234, the latter being adjustable in length by means of turn-buckles or the like. The rod 234 extends between and connects a pin 238 projecting radially from the shaft of the piston 136 to a second pin 242 extending outwardly of a principal surface of the moveable bevel gear 222, at an eccentric position thereon. Universal type connections are used in connecting or joining the opposite ends of the linkage 230 to the bevel gear and to the piston.

The operation of the machine will be evident from the foregoing detailed description. Valve action synchronized with and controlled by rotation of the floating rings causes opening and closing of the fluid supply and exhaust ports, the fluid being alternately admitted and exhausted from the cylinders at opposite ends of the cylinder and piston assemblies. The reciprocal action of the pistons in the cylinders drives the linkage 230 to rotate the bevel gears 222 whereby the spider 210 and the output shaft 50 connected thereto revolve or rotate. That is, the piston stroke and the controlled related linkages are arranged to effect rotation of the output shaft 50. Rotation of the output shaft 50 causes, in turn, rotation of the secondary shaft 92 through gears 86 and 90, and the secondary shaft drives the floating rings 76 and 78 through bevel gears 102 and 104 and gears 108 and 110 of the floating rings.

By reason of the angled disposition of the floating rings 76 and 78, during reciprocal action of the pistons 136 in their cooperating cylinders 130 and 132 and the consequent rotation of the output shaft and in turn the floating rings, the entire piston assemblies are moved laterally in an ordered manner, from side to side during operation of the engine. That is, as the floating rings 76 and 78 rotate obliquely with respect to the drive shaft 92, but in parallel planes, they carry the piston-cylinder assemblies in a circular orbit. At the same time, each piston-cylinder assembly extending between the opposed floating rings 76 and 78 undergoes a lateral shifting or back and forth movement correlated with the angular rotation of the rings. This novel arrangement contributes to the overall efliciency and power of the hydraulic machine.

The foregoing description and drawings are given merely to explain and illustrate the invention, and the manner in which it may be performed, and the invention is not to be limited thereto except insofar as the appended claims are so limited since those skilled in the art now have this disclosure before them Will be able to make modifications and variations therein without departing from the scope and spirit of the invention.

I claim:

1. A fluid-actuated hydraulic engine comprising a housing adapted to contain hydraulic fluid under pressure and having fluid input and fluid discharge means;

a primary shaft comprising an elongated output shaft journaled and rotatably supported on opposed walls of said housing,

an end of said output. shaft extending through a Wall of said housing for connection to a device to be coupled to said engine and to be driven thereby;

a pair of parallel laterally spaced floating rings, said floating rings comprising gears axially supported on said output shaft and carried on ball races for rotation of said rings on said output shaft;

principal planes defined by said floating rings intersecting said output shaft at equal angles other than 90";

a primary gear fixed on said output shaft and axially supported thereon and transversely thereof for rotation therewith;

a secondary shaft parallelly disposed with respect to said output shaft and constituting a drive shaft for rotating said floating rings,

gear means fixed on said drive shaft and meshing with said primary gear of said output shaft to mechanically and positively couple said secondary shaft to said output shaft;

a pair of laterally spaced bevel gears fixed on said drive shaft for positive rotation therewith,

each member of said pair of bevel gears meshing with respective said laterally spaced floating rings riding on said output shaft, whereby rotation of said output shaft causes rotation of said drive shaft and said floating rings coupled thereto;

a sleeve coaxial with and disposed as a bushing about said output shaft,

said sleeve being fixed to and extending transversely of and inwardly of a wall of said housing;

a stationary bevel gear fixed immovably on said sleeve;

a spider connected to said output shaft, arms of said spider extending radially and transversely of said output shaft and constituting stud shafts;

a movable bevel gear rotatably supported on each said stud shafts and meshing with said stationary bevel gear fixed on said sleeve;

a plurality of elongated cylinder and piston assemblies supported on and between said spaced floating rings and displaced radially outwardly of said output shaft and extended generally parallel thereto;

each said cylinder and piston assemblies comprising laterally spaced coaxial tubular cylinder sections and piston means coaxial with and slidably supported in said spaced cylinder sections for reciprocal movement therein,

joinder means at outer ends of said cylinder sections and adapted to connect said cylinders to said laterally spaced floating rings in fluid-sealing engagement therewith,

said outer ends of said cylinders being in communication with fluid supply and exhaust ports in said float ing rings for supplying pressurized fluid to displace said piston means and for exhausting fluid from said outer ends of said cylinders;

valve means controlling and regulating admission of non-compressible fluid into and exhaust of said fluid from said cylinder sections during reciprocal movement of said piston means in said cylinder sections;

sequentially operable control means for regulating programmed operation of said valve means to eifect and to coordinate said movement of said piston means;

linkage means attached to each said piston means intermediate ends thereof and to a corresponding said moveable bevel gear, carried on said arms of said spider, connection of said linkage means to said moveable bevel gear being at an eccentric position on a principal face of said gear;

movement of said piston means in response to fluid pressure applied thereagainst producing revolution of each said moveable bevel gear and rotation of said spider associated therewith to drive said output shaft and said principal gear carried thereby to rotate said second shaft and, in turn, said floating rings coupled thereto;

whereby during rotation of said floating rings said cylinder and piston assemblies carried thereby undergo lateral displacement and reciprocal lateral movement augmenting reciprocal movement of said piston means within said cylinder sections.

References Cited UNITED STATES PATENTS 657,409 9/1900 Gould 91198 2,706,384 4/1955 Schott 91175 2,957,462 10/1960 Clark 91-175 FOREIGN PATENTS 525,625 5/1931 Germany.

MARTIN P. SCHWADRON, Primary Examiner.

45 P. E. MASLOUSKY, Assistant Examiner. 

1. A FLUID-ACTUATED HYDRAULIC ENGINE COMPRISING A HOUSING ADAPTED TO CONTAIN HYDRAULIC FLUID UNDER PRESSURE AND HAVING FLUID INPUT AND FLUID DISCHARGE MEANS; A PRIMARY SHAFT COMPRISING AN ELONGATED OUTPUT SHAFT JOURNALED AND ROTATABLY SUPPORTED ON OPPOSED WALLS OF SAID HOUSING, AN END OF SAID OUTPUT SHAFT EXTENDING THROUGH A WALL OF SAID HOUSING FOR CONNECTION TO A DEVICE TO BE COUPLED TO SAID ENGINE AND TO BE DRIVEN THEREBY; A PAIR OF PARALLEL LATERALLY SPACED FLOATING RINGS, SAID FLOATING RINGS COMPRISING GEARS AXIALLY SUPPORTED ON SAID OUTPUT SHAFT AND CARRIED ON BALL RACES FOR ROTATION OF SAID RINGS ON SAID OUTPUT SHAFT; PRINCIPAL PLANES DEFINED BY DAID FLOATING RINGS INTERSECTING SAID OUTPUT SHAFT AT EQUAL ANGLES OTHER THAN 90*; A PRIMARY GEAR FIXED ON SAID OUTPUT SHAFT AND AXIALLY SUPPORTED THEREON AND TRANSVERSELY THEREOF FOR ROTATION THEREWITH; A SECONDARY SHAFT PARALLELLY DISPOSED WITH RESPECT TO SAID OUTPUT SHAFT AND CONSTITUTING A DRIVE SHAFT FOR ROTATING AND FLOATING RINGS, GEAR MEANS FIXED ON SAID DRIVE SHAFT AND MESHING WITH SAID PRIMARY GEAR OF SAID OUTPUT SHAFT TO MECHANICALLY AND POSITIVELY COUPLE SAID SECONDARY SHAFT TO SAID OUTPUT SHAFT; A PAIR OF LATERALLY SPACED BEVEL GEARS FIXED ON SAID DRIVE SHAFT FOR POSITIVE ROTATION THEREWITH, EACH MEMBER OF SAID PAIR OF BEVEL GEARS MESHING WITH RESPECTIVE SAID LATERALLY SPACED FLOATING RINGS RIDING ON SAID OUTPUT SHAFT, WHEREBY ROTATION OF SAID OUTPUT SHAFT CAUSES ROTATION OF SAID DRIVE SHAFT AND SAID FLOATING RINGS COUPLED THERETO; A SLEEVE COAXIAL WITH AND DISPOSED AS A BUSHING ABOUT SAID OUTPUT SHAFT, SAID SLEEVE BEING FIXED TO AND EXTENDING TRANSVERSELY OF AND INWARDLY OF A WALL OF SAID HOUSING; A STATIONARY BEVEL GEAR FIXED IMMOVABLY ON SAID SLEEVE; A SPIDER CONNECTED TO SAID OUTPUT SHAFT, ARMS OF SAID SPIDER EXTENDING RADIALLY SAND TRANSVERSELY OF SAID OUTPUT SHAFT AND CONSTITUTING STUD SHAFTS; A MOVABLE BEVEL GEAR ROTATABLY SUPORTED ON EACH SAID STUD SHAFTS AND MESHING WITH SAID STATIONARY BEVEL GEAR FIXED ON SAID SLEEVE; A PLURALITY OF ELONGATED CYLINDER AND PISTON ASSEMBLIES SUPPORTED ON AND BETWEEN SAID SAPACED FLOATING RINGS AND DISPLACED RADIALLY OUTWARDLY OF SAID OUTPUT SHAFT AND EXTENDED GENERALLY PARALLEL THERETO; EACH SAID CYLINDER AND PISTON ASSEMBLIES COMPRISING LATERALLY SPACED COAXIAL TUBULAR CYLINDER SECTIONS AND PISTON MEANS COAXIAL WITH AND SLIDABLY SUPPORTED IN SAID SPACED CYLINDER SECTIONS FOR RECIPROCAL MOVEMENT THEREIN, JOINDER MEANS AT OUTER ENDS OF SAID CYLINDER SECTIONS AND ADAPTED TO CONNECTED SAID CYLINDERS TO SAID LATERALLY SPACED FLOATING RINGS IN FLUID-SEALING ENGAGEMENT THEREWITH, 